Blade fabricating machine



April 5, 1960 F. SCHLEGEL 2,931,255

BLADE FABRICATING MACHINE Filed June 18, 1956 5 Sheets-Sheet 1 S! r \mu 0 W\ Q5 2 m \1 Ni ii '5, I E

INVENTOR.

FRED SCHLEGEL Mab@u ATTORNEYS April 5, 1960 F. SCHLEGEL 2,931,255

BLADE FABRICATING MACHINE Filed June 18, 1956 5 Sheets-Sheet 3 Fig.3.

IN VEN TOR.

FRED SCHLEGEL 7/L fi wig/r ATTORNEYS April '5, 1960 Filed June 18, 1956 F. SCHLEGEL BLADE FABRICATING MACHINE 5 Sheets-Sheet 4 Fig.4.

INVENTOR.

FRED SCHLEGEL ATTORNEYS April 5, 1960 F. SCHLEGEL 2,931,255

BLADE FABRICATING MACHINE Filed June 18, 1956 5 Sheets-Sheet 5 Fig.5

INVENTOR- FRED SCHLEGEL ATTORNEYS nite BLADE FABRICATING MACHINE This invention relates to a metallic blade rolling machine, such as turbine blades and the like, wherein the blades are rolled to a desired air foil section.

An object of this invention is to provide a machine for rapidly and efficiently rolling metallic blades.

Another object of this invention is to provide a blade rolling machine which insures prolonged life of metallic rolling dies.

These and other objects and advantages will become more apparent from the following detailed description of the device and from the accompanying drawings, wherein:

Figure 1 is a side view, partially in section, of the machine.

' Figure 2 is a side view showing difierent details of the machine. I Figure 3 is an end view of a portion of the machine.

Figure 4 is a schematic showing of the controls for the machine, and Figure 5 is another schematic showing of the machine controls.

Briefly, this machine is comprised of a frame and a pair of spaced die shafts rotatably mounted in eccentric bearings. A means is provided to selectively oscillate the eccentric bearings so that the die shafts can be selectively moved apart or closer together to a working position. An additional means is provided to oscillate the die shafts so that the dies carried by the shafts will perform an operation on a work piece interposed between the dies. A novel aspect of this machine relates to the structure to vary the distance between die shaft centers so that when the dies are being returned to a position for initiation of another cycle, the dies are spaced and therefore, are not subject to high surface loading between the contacting surfaces of the dies on return to the initial position.

Referring to the drawing for a more detailed description, a machine is comprised of a one piece cast steel main frame 12 having a base plate 14, vertical sections 16 and 18, and a top frame portion 20. Supporting legs 22 are provided to support a structure 24 which extends to one side of the main frame. A pair of upper eccentric bushings 26 and a pair of lower eccentric bushings 28 are. rotatably mounted in the main frame in bronze bearings 30 and 32, respectively. A pair of gears 34 are fixedly connected to upper eccentric bushings 26 and an identical pair of gears 36 are fixed to lower eccentric bushings 28 in a manner such that rotation of the gears results in rotation of the eccentric bushings. An upper die shaft 38, having a central portion 44), is rotatably mounted in eccentric bushings 26 by a pair of trunnions 42 and sleeve bearings 44 are interposed between the trunnions 42 and the eccentric bushings 26. .Similarly, a lower die shaft 46 is provided with a cen- .tates Patent O t ral portion 48 and a pair of trunnions 50 with said trunnions rotatably mounted in the eccentric bushings 28 by means of sleeve bearings 52. An upper rolling arm 54 is fixed to the upper die shaft 38 and a lower rolling arm 56 is fixed to the lower die shaft 46 so that oscillation of the rolling arms results in oscillation of the die shafts. A pair of upper thrust plates 58 are interposed between the end surfaces of trunnions 42 and the end surfaces of a pair of pressure plugs 60, which are adapted to be selectively slideable in cylindrical portions 62 of the main frame. A pair of pressure screw sleeves 64 are fixed in portions 66 of the main frame and have threadingly inserted therein pressure screws 68 which are locked in position by lock nuts 70. This structure provides for longitudinal positioning and adjustment of the upper die shaft 38. Similarly, a pair of thrust plates 72 are interposed between the end surfaces of trunnions 50 and the end surfaces of a pair of pressure plugs 74, which are adapted to be selectively slideable in cylindrical portions 76 of the main frame. A pair of pressure screw sleeves 78 are fixed in portions 80 of the main frame and have threadingly inserted therein pressure screws 82 which are locked in position by lock nuts 84. This structure provides for longitudinal positioning and adjustment of the lower die shaft 46. Die members 86 and 88 are carried by the upper die shaft 38 and the lower die shaft 46, respectively.

A pair of longitudinally movable racks 90 are dis posed between and in meshing engagement with the gears 34 and 36 so that longitudinal movement of the racks etfects rotary movement of gears 34, 36 and eccentric sleeves 26, 28. A hydraulic feed cylinder assembly 92 is provided with a rod and piston assembly 94 which is connected to the end of one of the racks 90. A rotatable shaft 96 has fixed thereto a pair of spaced gears 98 which mesh with the spaced racks 90 and func tion as the synchronizing means between the spaced racks 90. When the piston 94 moves one of the racks 90 longitudinally, this motion is transmitted to the other rack 90 through the interconnection of shaft 96 and gears 98.

In order to accurately space the distance between the dies 86 and 88, the racks 90 must be stopped at precisely the same position for each cycle of operation. This function is accomplished by providing a stop screw 100 which is suitably connected to an indicator assembly 102, which indicates the exact position of end 104 of the stop screw. A handwheel 196 is provided to effect rotation of the stop screw to a given longitudinal posi-. tion. It is obvious, therefore, that the longitudinal movement of the racks 90 is limited by abutment of end 108 of one of the racks with the end 104 of the stop screw.

The upper rolling arm 54 has pivotally connected thereto at 110 a link 112 and this link has pivotally connected thereto at 114 a drive crank 116 which is fixed to a drive gear 118. The lower rolling arm 56 has pivq otally connected thereto at 120 a link 122 and this link has pivotally connected thereto by a pin 124, an adjustable drive crank 126 which is fixed to a drive gear 128. An adjusting screw 13! is longitudinally fixed to an adjustment slide inside link 122 and is threadingly engaged with a link end plate 132 to longitudinally position the adjustment slide. The adjustment slide is fixed to pin 124 so that longitudinal adjustment of the slide determines the efiective length of link 122. A look nut 134 is provided to lock screw in the adjusted position. A longitudinally movable rack 136 is inter posed between drive gears 118 and 128 and meshes with these drive gears. A piston 138 of hydraulic roll cylinder assembly 140 is connected to the end of rack 136 and when the rack 136 is reciprocated by actuation of the roll cylinder, the longitudinal movement of rack 136 is transmitted into rotational movement of drive gears 118 and 128. I

Figure 4 schematically illustrates the control structure in the operation of the rolling machine. The piston 94 of feed cylinder assembly 92 is provided with a suitable control arm 142,and the piston 138 of roll cylinder as sembly 148 is provided with a similar control arm 144. A pair of limit switches 146 and 148 are arranged on the frame in a manner such that when the feed cylinder assembly piston 94 is moved forward to a position for rnoving the dies closer together, the limit switch 148 is actuated. When the piston 94 is moved to a position in which thedies are spaced farthest apart, the limit switch 146 is actuated. Similarly, a pair of limit switches 158 and 152 are provided on the frame in relation'to the roll cylinder assembly 148 such that when the piston 138 is moved forward or to a position in which the blade rolling has been completed, the limit switch 150 is actuated and when piston 138 is moved to a position in which the dies are positioned for a new rolling cycle, the limit switch 152 is energized.

An oil pump 168 is provided to selectively supply fluid pressure to the feedcylinder 92 and roll cylinder 140 through an arrangement of solenoid operated valves V which are connected in the following manner. A con-.

duit 162 communicates with a pair of conduits 164 and sump 1 84 and a conduit 186 which communicates with the conduit 1 88 and a conduit 190. The conduit 188 is connected to avalve 192 comprising a cylinder portion 19 4,"a piston 196, and a spring 198 which is positioned tourge the piston in a line blocking position as shown in Figure 4. The rod portion of piston 196 and coil 200 4 V Figure 5 schematically illustrates the functional relationship between the limit switches 146, 148, 150, and 152, the solenoids 214, 178, 230, 202, and start button 250. In Figure 5, the solid line connections between the limit switchesand the solenoids represent an energization of the solenoids by the limit switch to which the solid line is connected. The broken or dotted lines indicate that the particular solenoid connected by the dotted line is deenergized by the limit switch to which the dotted line is connected. For example, limit switch 148 energizes solenoid 214 and deenergizes solenoid 178. To clarify the understanding of the operation, the positions of the limit switches and solenoids in Figure .5 is approximately in the same location as shown in Figure 4. The deviceroperates in the following manner.

Referring to Figures l and 5, when the start button" 258 is pressed, solenoids 178 and 230 are energized,

' which results in a flow of fluid pressure through conduits 162, 164, valve 168, conduits 186, 188, and 240 to the blind end of feed cylinder 92, and fluid flows out of the rod end of cylinder 92, through conduit 24 2, valve 222,

and conduit 244m sump. 184. Consequently, piston 9.4

is moved to the right as viewed in Figure 4, which results 'in moving rack 98 to the right, as viewed in Figure'Z.

Movement ofthe rack results in rotational movement'of gears 34 and 36, which movement results in the moving of dies 86 and 88 to a working position.

When the rod 94 reaches the end of its travel, the projection142 contacts limit switch 148. Asiudicate'din Figure 5, limit switch 148 energizes solenoid 214 and de'energizes solenoid 178. Since solenoid 230 remains energized, the blind end of cylinder '92 remains'pressurized and holding pressure pump 246 replaces any fluid which might be lost around the piston seal. When the solenoid 214 is energized, fluid pressure is allowed to flow from conduit 166 through valve 170, to the-conduit 220,.and into the blind endof roll cylinder 140, and fluid form a solenoid 202 which controls the opening and I 7 closing of valve 192. A conduit 204 also communicates with the valve 192 and is connected to the rod side of the cylinderassembly 148. A check valve 206 is provided.

in the conduit 190 which allows fluid to flow from. conduit 204 through conduit 190 to conduit 186, but prevents'the flow of fluid from conduit 186 to conduit 204 is connected to the'blind side of the cylinder assembly 140. Theconduit 188 also communicates, with a four-, 7

' beingvplaced in communication with the sump 184 and way valve 222 which is provided with a body portion 224 A spring 234 is arranged to urge the piston 226 to the' right, as viewed in Figure 4. A check valve 238 is'in:

' 92 through conduit 164, valve 168," conduits 1 86, 1 88,

valve'222, and conduit 242, and fluid 'drainsQf m the blind end of cylinder 92 through conduit"24t l,, valve terposed in the conduit 188 so that fluid is allowed to flow from conduit 188 to the valve 222, but is prevented from flowing in the opposite direction. A conduit 240 provides communication between the four-way valve and connects the four-way valve and the rod end of the feed cylinder 92. The four-way'valve and the sump 184 are connected by means of conduit 244. A holding pressure pump 246 is connected to the blind end of feed cylinder 92 by means of a conduit 248 to provide fluid to the blind end of feed cylinder 92 so that the rod and piston r the blind end of feed cylinder 92, and a conduit 242 flows out of the rod end of cylinder through con-- du'its 2 04, 194), valve 168, and conduit 182 to the sump.

Consequently,'the piston and rod assembly 138 is moved to the right as viewed in Figure l, which results in movement of rack'136 to the right. Since rack 136 meshes with driving gears 118 and 128, driving cranks 116 and 126 are rotated in a counterclockwise direction which transmits counterclockwise rotation through links 112 and'122, respectively, to therolling arms .54 and 5 6, This counterclockwise rotation of the rolling arms '54 and 56 results in a rolling operation being performed on the work piece which is interposed between dies 86 and 88. Completion of the movement of rod 138to extended position completes the rolling operafiqll 31 9 when such position is reached, the projection con;-

tacts limit switch 150.

Limit switch deenergizes solenoids 214an'd 230 and energizes solenoid 178 and deenergization of solenoid 214 results in the blind side of rod;cylinder- I .40

deenergization of solenoid 230Iresults in the communication of conduit 242 with the input conduit 188, Since solenoid 178 has also been energized fluid pressure is therefore introduced'into the rod end of ffed cylinder 222,, and conduit 244 into the sump. Therefore, the piston rod assembly94is movedback intothe feed cylinder 92 which 'results in a separationof thedies rod end'ofroll cylinder 140 through conduit .164,va:l-ve

168, 'conduit's1186, 188, valve .192, and conduit 204, which: results in thereturn of the rack 136 to" the initial position and the rolling arms 54 and 56 to the initial position. When this motion is completed, limit switch 152 is contacted. Limit switch 152 deenergizes solenoid 178 and solenoid 202 which completes the semiautomatic operating cycle.

Obviously, this operation cycle can also be effected by manual operation, that is, the operator first energizes solenoid 178 and solenoid 230 by pressing the starter button 250. This results in movement of the dies to a proximate or Working position. Next, solenoid 178 is deenergized and solenoid 214 is energized which effects the rolling operation. Next, the dies are moved to a spaced position by deenergizing solenoids 214 and 230, and energizing solenoid 178. The rolling arms are then returned to the initial position by energizing solenoid 202, leaving solenoid 178 in an energized position. After this motion is effected, the cycle is completed by deenergizing solenoid 178 and solenoid 202.

From the above description of the structure and operation of this machine, it is obvious that a structure has been conceived wherein a rolling operation can be performed on a work piece, preferably a turbine blade, wherein the dies have long life and the machine is rapid and efiective in operation.

While the present invention has been described in connection with certain specific embodiments, it is to be understood that the foregoing description is merely exemplary and that the concept of this invention is susceptible of numerous other modifications, variations, and applications which will be apparent to persons skilled in the art. The invention is to be limited, therefore, only by the broad scope of the appended claims.

What I claim is:

1. A rolling machine comprising a frame, means mounted on said frame carrying a pair of rolling dies, shaft portions integral with said dies, eccentric means for selectively moving said die carrying means and said dies to a spaced position or to a work operating position, said eccentric means comprising sleeves having inner and outer annular surfaces disposed eccentrically with respect to each other, said outer surfaces journalled in said frame, said shaft portions journalled on said inner surfaces and being freely rotatable with respect to said sleeves, means to selectively oscillate said die carrying means and said dies, first control means to sequentially operate first power means to rotate said eccentric means to move said die carrying means to a work operating position, second control means to next operate second power means to arcuately move said die carrying means in a Work performing direction, third control means to next operate said first power means to rotate said eccentric means to move said die carrying means to a spaced position, and fourth control means to next operate said second power means to arcuately move said die carrying means in a direction opposite to said work performing direction.

2. A rolling machine comprising a frame, a pair of dies positioned to perform a rolling operation on a work piece, means carried by said frame to support said dies, means operably connected to said die supporting means to selectively oscillate said dies and said die supporting means, eccentric means disposed in supporting relationship between said die supporting means and said frame and being rotatable with respect to said die supporting means to selectively reciprocate said die supporting means in a direction normal to the oscillating axes of said die supporting means, first control means to sequentially operate first power means to rotate said eccentric means to move said die supporting means to a work operating position, second control means to next operate second power means to arcuately move said die supporting means in a work performing direction, third control means to next operate said first power means to rotate said eccentric means to move said die supporting means in a direction away from each other, apd fourth control '5 means to next operate said s'econd power means to arcuately move said die supporting means in a direction opposite to said work performing direction.

3. A rolling machine comprising" a frame, a pair of rolling arms, cooperating rolling dies carried by said rolling arms, laterally spaced gear means, eccentric bushing means. connected for rotation with said gear means and journalled in annular openings in said frame, an annular internal portion of each of said bushing means disposed eccentrically to said annular openings in said frame, shaft portions integral with each of said rolling arms and being journalled in said annular internal portion of each of said bushing means, a first reciprocable rack means meshing with said laterally spaced gear means, means to reciprocate said first rack means, first crank means, gear means fixed to said first crank means, second crank means, gear means fixed to said second crank means, first link means connecting said first crank means with one of said rolling arms, second link means connecting said second crank with the other of said rolling arms, second rack means meshing with said gear means fixed to said crank means and means to reciprocate said second rack means.

4. A machine, according to claim 3, wherein said means to reciprocate said first rack means comprises a hydraulic piston and cylinder means, a pair of spaced limit switches operable by said piston means, and said means to reciprocate said second rack means comprises a hydraulic piston and cylinder means, electrical means operated by said limit switches, hydraulic control means sequentially operable by said electrical means to se quentially operate said hydraulic piston and cylinder means.

5. A rolling machine comprising a frame, a pair of rolling arms, cooperating rolling dies carried by said rolling arms, laterally spaced gear means, eccentric bushing means connected for rotation with said gear means and journalled in annular openings in said frame, an annular internal portion of each of said bushing means disposed eccentrically to said annular openings in said frame, shaft portions integral with each of said rolling arms and being journalled in said annular internal portion of each of said bushing means, a first reciprocable rack means meshing with said laterally spaced gear means, means to reciprocate said first rack means, first crank means, gear means fixed to said first crank means, second crank means, gear means fixed to said second crank means, first link means connecting said first crank means with one of said rolling arms, second link means connecting said second crank with the other of said rolling arms, a second rack means meshing with said gear means fixed to said crank means and means to reciprocate said second rack means, switch means controlled by said means to reciprocate said first rack means, valve means controlled by said switch means and said valve means controlling movement of said means to reciprocate said first rack means.

6. In a rolling machine, a frame an upper die-carrying means, a lower die-carrying means, annular portions integral with said die carrying means, means operably interconnecting said upper die-carrying means and said lower die-carrying means, means to actuate said interconnecting means, eccentric means operable to move said upper die-carrying means away from said lower diecarrying means, eccentric means operable to move said lower die-carrying means away from said upper diecarrying means, said eccentric means comprising sleeves having inner and outer annular surfaces disposed eccentn'cally with respect to each other, said outer surfaces journalled in said frame, said annular portions of said die carrying means journalled on said inner surfaces and being freely rotatable with respect to said sleeves, means operably interconnecting said first eccentric means with said second eccentric means, means to actuate said lastmentioned means and control means to sequentially @Cilh ate said first actuating-meahs and said second actuating "1,841,229 means; Q 7 V 3,554,271 t??? 6*??? wk 6f rm 1 fiZZi UNITED STATES PATENTS 5 r 741,685 Webb Ja -:4. em. 13, 1903 Great Britain ,Ja n. 15 1925 

